EP2085632B2 - Agencement d'embrayage double - Google Patents

Agencement d'embrayage double Download PDF

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Publication number
EP2085632B2
EP2085632B2 EP09150546.1A EP09150546A EP2085632B2 EP 2085632 B2 EP2085632 B2 EP 2085632B2 EP 09150546 A EP09150546 A EP 09150546A EP 2085632 B2 EP2085632 B2 EP 2085632B2
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EP
European Patent Office
Prior art keywords
dual clutch
arrangement
friction
shaft
input member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP09150546.1A
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German (de)
English (en)
Other versions
EP2085632A1 (fr
EP2085632B1 (fr
Inventor
Kuno Fronius
Jan Hasenkamp
Salvatore Gaggia
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Magna PT BV and Co KG
Original Assignee
Getrag Getriebe und Zahnradfabrik Hermann Hagenmeyer GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Application filed by Getrag Getriebe und Zahnradfabrik Hermann Hagenmeyer GmbH and Co filed Critical Getrag Getriebe und Zahnradfabrik Hermann Hagenmeyer GmbH and Co
Publication of EP2085632A1 publication Critical patent/EP2085632A1/fr
Application granted granted Critical
Publication of EP2085632B1 publication Critical patent/EP2085632B1/fr
Publication of EP2085632B2 publication Critical patent/EP2085632B2/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/12—Clutch systems with a plurality of electro-magnetically-actuated clutches

Definitions

  • the present invention relates to a dual clutch assembly for a dual clutch transmission for motor vehicles, having a first and a second friction clutch having a common input member and an output member, wherein the output member of the first friction clutch is connected to a first shaft and wherein the output member of the second friction clutch is connected to a second shaft which is formed as a hollow shaft concentrically around the first shaft, wherein the first and the second friction clutch are radially interleaved.
  • a dual clutch arrangement is known from the document DE 10 2004 061 020 A1 wherein a vibration damper assembly for damping unwanted vibrations is disposed radially outside of the friction clutches.
  • Dual clutch transmissions are well known. They include a dual-clutch arrangement with two friction clutches and a stepped transmission with two parallel partial transmissions. A branch with a first friction clutch and a first partial transmission, the odd gear ratios are assigned. On the input side, the friction clutches are connected to a drive motor, for example an internal combustion engine, a hybrid drive unit or the like.
  • the partial transmissions are usually realized as a spur gear. The connection of the friction clutch assembly with the partial transmissions takes place via a shaft arrangement with an inner shaft and a hollow shaft arranged concentrically therewith.
  • the actuators used for this purpose may be hydraulic or electrical actuators.
  • the input member of the friction clutches is mounted on the housing, thereby enclosing a space through which cooling and lubricating oil is discharged.
  • the friction clutches are designed as wet running Lamellenkupptungen.
  • the vibration damper assembly is disposed radially outside of the friction clutches and also formed wet running.
  • a dual clutch arrangement in which the friction clutches are nested radially into one another and a vibration damper assembly is arranged in the axial direction in front of the friction clutches.
  • a common input member of the two friction clutches is mounted on the second shaft, wherein a shaft portion of the Eingsngsgliedes extends in the axial direction to the rear.
  • a generic dual clutch assembly is made WO-A-63/006840 known.
  • the dual clutch assembly according to the invention can be constructed axially very short design.
  • the two friction clutches are nested radially one inside the other, that is, they are not arranged axially next to one another.
  • the input member is radially supported on the second shaft. This also allows an axially compact design.
  • the vibration damper assembly is provided within a housing of the dual clutch assembly, so that not necessarily a wide vibration damper assembly (such as a Zwelmassenschwungrad) must be provided outside the housing.
  • a wide vibration damper assembly such as a Zwelmassenschwungrad
  • the arrangement radially outside of the friction clutches can be realized in the axial direction at least a certain overlap with the friction clutches, so that an axially short design is promoted.
  • vibration damper assembly is aligned axially with the friction clutches.
  • the vibration damper assembly is arranged in the axial direction completely or largely overlapping with the Rebkupplept, so that a short axial design results.
  • a vibration damper arrangement for damping unwanted vibrations is arranged laterally next to the friction clutches.
  • a vibration damper assembly is provided outside a housing of the dual clutch assembly.
  • the vibration damper assembly belsplelieri be designed as a two-mass Schwugrad. This embodiment is preferred if strong installation space limitations are present in the area of the double clutch.
  • the bearing arrangement for supporting the input member on the second shaft is arranged radially inside the friction clutches.
  • the axial design can be shortened even further, especially if the vibration damper assembly is aligned axially with the friction clutches.
  • the input member is axially supported on the second shaft. In this way it is possible to use the input member as a bearing for actuator arrangements.
  • a bearing arrangement for the radial and axial mounting of the input member on the second shaft to a single bearing.
  • the input member structurally relatively easy to be realized.
  • the terms "in the axial direction front or rear" should refer to the drive side and the output side of the dual clutch assembly.
  • a bearing arrangement for supporting the input member on the second shaft in the axial direction between the output members of the friction clutches is arranged.
  • the bearing assembly may optionally be simplified, since the input member also extends in the axial direction between the output members of the friction clutches and thus can be axially mounted thereon.
  • the input member has a radial portion which is arranged in the axial direction behind the friction clutches.
  • the radial section of the input member has at least one opening through which at least one actuator arrangement can actuate at least one of the friction clutches.
  • the actuator assemblies may include hydraulic or electrical actuator assemblies, such as those shown in Figs. electro-hydraulic, electromechanical, electromotive and / or electromagnetic actuators.
  • the input member is connected to a drive member of the dual clutch assembly.
  • the input member may be rigidly connected to a drive member of the dual clutch assembly.
  • the dual clutch assembly may also be provided without vibration damper assembly.
  • the input member is connected via the vibration damper assembly with the drive member.
  • the input member may extend, for example in the axial direction behind the friction clutches and the drive member may be arranged in the axial direction in front of the friction clutches or the vibration damper assembly.
  • the drive member has a shaft section which extends out of a housing of the dual clutch arrangement.
  • the shaft portion may be connected to the drive side, for example with a crankshaft or a flywheel of the associated drive train.
  • the first shaft is radially mounted on the shaft portion of the drive member.
  • the second shaft may for example be mounted on the first shaft.
  • the drive member has a radial portion, wherein between the output member of the first friction clutch and the radial portion, a first thrust bearing is arranged.
  • the first thrust bearing can serve to absorb axial forces that occur during the actuation of the first friction clutch.
  • a second thrust bearing is arranged between the output member of the first friction clutch and a member of the second friction clutch.
  • the second thrust bearing can also absorb forces that arise during the actuation of the second friction clutch.
  • the member of the second friction clutch may be a member fixedly connected to the input member, such as an input disk carrier, or may be an output member.
  • the output member of the first friction clutch is arranged radially inward.
  • a radially inner output member may be an inner disk carrier.
  • the output member of the first friction clutch is arranged radially outward.
  • the output member of the second friction clutch is arranged radially inward.
  • the output member of the second friction clutch may also be arranged radially on the outside.
  • first friction clutch is arranged radially outside the second friction clutch and / or if the friction clutches are designed as wet-running friction clutches.
  • the arrangement of the vibration damper assembly within the housing of the dual clutch assembly preferably means that the vibration damper assembly is formed wet running.
  • a dual-clutch arrangement can be realized which is suitable for installation in front-transverse drive trains of motor vehicles. Due to the use of wet-running friction clutches comparatively high torques can be transmitted.
  • the arrangement of the vibration damper radially outside or laterally adjacent to the friction clutches possibly enables better protection of the vibration damper. Overall, an integrated design of the friction clutches and the vibration damper arrangement can be realized. Also, the number of components can be reduced, in particular the number of thrust bearings and / or axial fasteners of the friction clutch (s).
  • a powertrain for a motor vehicle is shown schematically and generally designated 10.
  • the drive train 10 is designed as an axially short drive train in particular for the front-transverse installation designed.
  • the drive train 10 includes a drive motor 12, such as an internal combustion engine or a hybrid drive unit and a dual-clutch transmission 14.
  • the dual clutch transmission 14 has a first part of a transmission 16 and a second partial transmission 18 in a conventional manner.
  • the partial transmissions 16, 18 are in Fig. 1 only schematically shown in the form of a respective wheelset.
  • the dual clutch transmission 14 includes a dual clutch assembly 20.
  • the dual clutch assembly 20 includes a housing 22 having a first housing wall 24 and a second housing wall 26.
  • the first housing wall 24 is a front housing wall adjacent to the drive motor 12.
  • the second housing wall 26 is a rear housing wall adjacent to the partial transmissions 16, 18th
  • the drive motor 12 is connected to a flywheel 28 which is mounted outside the housing 22 and which includes a starter toothing 30 on its outer circumference.
  • the crankshaft of the drive motor 12 is shown at 32 and fixedly connected to the flywheel 28.
  • the dual clutch assembly 20 includes a drive member 34 that includes a shaft portion 36.
  • the shaft portion 36 extends through the first housing wall 22 and is fixedly connected to the flywheel 28.
  • On the outer circumference of the shaft portion 36 is sealed by a shaft seal 38 relative to the housing 22.
  • the drive member 34 further includes a radial portion 40 which extends radially outward from the shaft portion 36 in the interior of the housing 22.
  • the dual clutch assembly 20 further includes a first friction clutch 42 and a second friction clutch 44 disposed radially nested one inside the other.
  • the friction clutches 42, 44 may each be designed as multi-plate clutches, in particular as wet-running multi-plate clutches.
  • the first friction clutch 42 is disposed radially outwardly of the second friction clutch 44, concentric therewith.
  • the input member 46 is connected to the drive member 34 via a vibration damper assembly 52 disposed radially outwardly of the first friction clutch 42 and axially aligned therewith.
  • the vibration damper assembly 52 comprises, in a manner known per se, spring means 54 which are designed to damp undesirable vibrations which are generated, for example, by the drive motor 12.
  • the vibration damper assembly 52 may also include other functions in a conventional manner.
  • the dual clutch assembly 20 further includes a first shaft 56, which is formed as an inner shaft, and a second shaft 58, which is arranged as a hollow shaft concentrically around the first shaft 56 around.
  • the first shaft 56 is connected to a first transmission input shaft 60 of the first partial transmission 16.
  • the second shaft 58 is connected to a second transmission input shaft 62 of the second partial transmission 18.
  • a common output shaft of the partial transmissions 16, 18 can be connected in a manner known per se to a mechanical differential, in particular a front axle differential and / or a torque vectoring arrangement or a twin clutch, in order to drive the wheels in the region of the front axle.
  • the first friction clutch 42 has a first output member in the form of a first output disk carrier 64.
  • the second friction clutch 44 has a second output member in the form of a second output disk carrier 66.
  • the input disk carriers 48, 50 are designed as outer disk carriers, and the output disk carriers 64, 66 are designed as inner disk carriers.
  • the first output disk carrier 64 is connected to the first shaft 56 via a radial section.
  • the second output disk carrier 66 is connected to the second shaft 58 via a radial section.
  • the input member 46 has an axially extending stub shaft 68.
  • the stub shaft 68 extends forward from the radial portion 47 of the input member 46, in such a way that the stub shaft 68 is arranged substantially radially inside the second friction clutch 44.
  • the dual clutch assembly 20 is axially mounted on the second shaft 58, via a bearing assembly 70th
  • the bearing assembly 70 is configured as a combined axial / radial bearing and configured to radially support both the dual clutch assembly 20 and to receive axial forces introduced into the input member 46.
  • the shaft portion 36 of the drive member 34 is mounted via a radial bearing 72 on the first shaft 56, preferably axially seen in the shaft seal 38.
  • the first shaft 56 extends for this purpose in the axial direction to the rear beyond that portion in which the first output plate carrier 64 is connected to the first shaft 56.
  • a first thrust bearing 74 is provided between the drive member 34 and a radial portion of the first output disk carrier 64.
  • a second thrust bearing 76 is provided between a radial portion of the first output disk carrier 64 and a radial portion of the second output disk carrier 66.
  • the thrust bearings 74, 76 are used to absorb forces caused by the operation of the friction clutches 42,44. Since the drive member 34 is rigidly connected to the already axially mounted flywheel 28, the axial forces can thus be introduced into a thrust bearing of the wheel 28, which in Fig. 1 however, for reasons of clarity is not shown.
  • a first actuator arrangement 78 and a second actuator arrangement 80 are provided which can exert respective forces F A1 and F A2 on the slats of the friction clutches 42, 44 in the axial direction.
  • the actuator arrangements 78, 70 are in Fig. 1 merely schematically shown, but are seen in the axial direction behind the two friction clutches 42, 44 and disposed behind the input member 46, preferably within the housing 22.
  • the actuator assemblies 78, 80 may be hydraulic or electrical actuator assemblies, in particular electro-hydraulic, electromotive or electromagnetic actuator assemblies.
  • the input member 46 has a first opening 82 through which the first actuator assembly 78 can actuate the first friction clutch 42. Furthermore, the input member 46 has a second opening 84, through which the second actuator assembly 80 can actuate the second friction clutch 44.
  • the friction clutches 42, 44 are designed in particular as a wet-running multi-plate clutches.
  • the associated fluid supply for lubrication and cooling purposes is in Fig. 1 not shown for reasons of clarity.
  • the lubricating fluid which is typically emitted from radially inward, is passed through the centrifugal forces by the friction clutches 44, 42 and finally also through the vibration damper arrangement 52.
  • the fluid is discharged to the rear due to an inclined top surface of the housing 22, namely into a sump, which may be divided into two in the axial direction in order to avoid seizing losses of the dual clutch arrangement 20.
  • the actuator assemblies 78, 80 may be formed as a single-acting actuator assemblies, wherein the friction clutches 42, 44 open automatically when not in operation by the radially outwardly flowing lubricating or cooling fluid.
  • FIGS. 2 to 6 alternate embodiments of dual clutch assemblies 20 according to the invention are shown.
  • the dual-clutch assemblies described below are generally identical in construction and operation to those described above with respect to FIG Fig. 1 described double clutch arrangement.
  • the same elements are therefore designated by the same reference numerals. In the following, only the differences are explained.
  • Fig. 2 is a dual clutch assembly 20 'shown, in which the second input disk carrier 50' is formed as an inner disk carrier, and in which the second output disk carrier 66 'is formed as an outer disk carrier.
  • Fig. 3 is shown a further embodiment of a dual clutch assembly 20 "according to the invention, which differs from the embodiment of the Fig. 1 differs in that the first input disk carrier 48 "is formed as an inner disk carrier and the first output disk carrier 64" as an outer disk carrier.
  • both input disk carrier 48 “', 50"' formed as an inner disk carrier
  • both output disk carrier 64 “', 66”' are formed as outer disk carrier.
  • a further dual clutch arrangement 20 iv is shown, which differs from the embodiment of the Fig. 1 differs in that the input member 46 iv has a further radial portion which extends axially in front of the second friction coupling 44 iv and is connected to a stub shaft 68 iv .
  • the stub axle 68 extends iv in the axial direction from the front portion of the input member 46 iv backwards, under the second friction clutch 44 iv .
  • the second thrust bearing 76 iv is disposed in this embodiment between the forward portion of the input member 46 iv and the radial portion of the first output disk carrier 64 iv and is located radially slightly further out than in the embodiment of Fig. 1 ,
  • Fig. 6 shows a further dual clutch assembly 20 v , which is substantially the dual clutch assembly 20 iv of Fig. 5 equivalent.
  • the double clutch assembly 20 v 48 v designed as an internal disk carrier and the first output disk carrier 64 v is designed as outer disk carrier.
  • FIGS. 7 and 8th shown alternative embodiments of dual clutch assemblies 20 VI and 20 VII .
  • the general structure of the dual clutch assembly 20 VI corresponds to the Fig. 7 the dual clutch assembly 20 of the Fig. 1 that includes a first friction clutch 42 and a second friction clutch 44.
  • a vibration damper arrangement 52a is not provided axially aligned with the friction clutches 42, 44, but laterally next to the friction clutches 42, 44.
  • the vibration damper arrangement 52a is provided between an input-side housing wall and the friction clutches 42, 44.
  • the lateral arrangement of the vibration damper assembly 52a and 52b, respectively, enables a reduction in the radial dimensions of the dual clutch assembly.
  • the flow of the first friction clutch 42 can be improved if it is designed as a wet-running clutch.
  • the dual clutch assembly 20 VII corresponds in its basic structure of the dual clutch assembly 20 IV of Fig. 5 However, similar to the dual clutch assembly 20 VI , the vibration damper assembly 52 a laterally adjacent to the friction clutches 42 IV , 44 IV is arranged. Also in this embodiment, although not shown, the vibration damper assembly may be disposed axially behind the friction clutches 42 IV , 44 IV .
  • FIGS. 9 and 10 Two further alternative embodiments of dual clutch assemblies 20 VIII and 20 IX are shown in which a vibration damper assembly 90 is provided outside a housing 22 of the respective dual clutch assembly.
  • the vibration damper assembly 90 may thus be configured as a "dry" damper assembly, such as a dual mass flywheel. Further, the vibration damper assembly 90 may include a starter ring gear as shown in FIGS FIGS. 9 and 10 is shown schematically radially on the outside.
  • the dual clutch assembly 20 VIII otherwise corresponds with respect to the further construction of the dual clutch assembly 20 of Fig. 1 comprising a first friction clutch 42 and a second friction clutch 44.
  • the basic structure of the dual clutch assembly 20 IV equal to 20 IX that the dual clutch arrangement Fig. 5 comprising a first friction clutch 42 IV and a second friction clutch 44 IV .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Claims (11)

  1. Agencement d'embrayage double (20) pour une transmission à embrayage double (14) pour véhicules automobiles, comprenant un premier et un deuxième embrayage à friction (42, 44), qui présentent un organe d'entrée commun (46) et un organe de sortie respectif (64, 66), l'organe de sortie (64) du premier embrayage à friction (42) étant relié à un premier arbre (56) et l'organe de sortie (66) du deuxième embrayage à friction (44) étant relié à un deuxième arbre (58), qui est réalisé sous forme d'arbre creux disposé concentriquement autour du premier arbre (56), le premier et le deuxième embrayage à friction (42, 44) étant emboîtés radialement l'un dans l'autre, l'organe d'entrée (46) étant supporté radialement sur le deuxième arbre (58) au moyen d'un agencement de palier (70),
    l'agencement de palier (70) pour supporter l'organe d'entrée (46) étant disposé sur le deuxième arbre (58) radialement à l'intérieur des embrayages à friction (42, 44), de telle sorte que l'agencement de palier (70) soit orienté axialement avec les embrayages à friction (42, 44), caractérisé en ce que l'organe d'entrée (46) est supporté axialement sur le deuxième arbre (58), l'agencement de palier (70) pour le support radial et axial de l'organe d'entrée (46) sur le deuxième arbre (58) présentant un palier unique.
  2. Agencement d'embrayage double selon la revendication 1, caractérisé par un agencement d'amortisseur d'oscillations (52) pour amortir les oscillations indésirables, lequel agencement d'amortisseur d'oscillations est disposé radialement à l'extérieur des embrayages à friction (42, 44).
  3. Agencement d'embrayage double selon la revendication 1, caractérisé par un agencement d'amortisseur d'oscillations (52) pour amortir les oscillations indésirables, lequel agencement d'amortisseur d'oscillations est disposé latéralement à côté des embrayages à friction (42, 44).
  4. Agencement d'embrayage double selon la revendication 1, caractérisé par un agencement d'amortisseur d'oscillations (90) en dehors d'un boîtier (22) de l'agencement d'embrayage double (20).
  5. Agencement d'embrayage double selon l'une quelconque des revendications 1 à 4, caractérisé en ce que l'organe d'entrée (46) présente une portion radiale (47) qui est disposée dans la direction axiale derrière les embrayages à friction (42, 44).
  6. Agencement d'embrayage double selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les embrayages à friction (42, 44) sont associés à au moins un agencement d'actionneur (78, 80) qui est disposé dans la direction axiale derrière l'organe d'entrée (46).
  7. Agencement d'embrayage double selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'organe d'entrée (46) est relié à un organe d'entraînement (34) de l'agencement d'embrayage double (20).
  8. Agencement d'embrayage double selon la revendication 7, caractérisé en ce que l'organe d'entrée (46) est relié à l'organe d'entraînement (34) par le biais d'un agencement d'amortisseur d'oscillations (52).
  9. Agencement d'embrayage double selon la revendication 7 ou 8, caractérisé en ce que l'organe d'entraînement (34) présente une portion d'arbre (36) qui s'étend hors d'un boîtier (22) de l'agencement d'embrayage double (20).
  10. Agencement d'embrayage double selon l'une quelconque des revendications 7 à 9, caractérisé en ce que l'organe d'entraînement (34) présente une portion radiale (40), un premier palier axial (74) étant disposé entre l'organe de sortie (64) du premier embrayage à friction (42) et la portion radiale (40).
  11. Agencement d'embrayage double selon l'une quelconque des revendications 1 à 10, caractérisé en ce qu'entre l'organe de sortie (64) du premier embrayage à friction (42) et un organe (66 ; 66' ; 66" ; 66"' ; 50iv ; 50v) du deuxième embrayage à friction (44) est disposé un deuxième palier axial (76).
EP09150546.1A 2008-02-01 2009-01-14 Agencement d'embrayage double Expired - Fee Related EP2085632B2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008008062.4A DE102008008062B4 (de) 2008-02-01 2008-02-01 Doppelkupplungsanordnung

Publications (3)

Publication Number Publication Date
EP2085632A1 EP2085632A1 (fr) 2009-08-05
EP2085632B1 EP2085632B1 (fr) 2013-07-03
EP2085632B2 true EP2085632B2 (fr) 2016-07-20

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EP09150546.1A Expired - Fee Related EP2085632B2 (fr) 2008-02-01 2009-01-14 Agencement d'embrayage double

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Country Link
US (1) US8413779B2 (fr)
EP (1) EP2085632B2 (fr)
CN (1) CN101498343B (fr)
DE (1) DE102008008062B4 (fr)

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DE102011122741B4 (de) * 2010-12-21 2021-01-28 Borgwarner Inc. Kupplungseinrichtung
CN102537120B (zh) * 2010-12-21 2016-04-13 博格华纳公司 离合器装置
DE102014205506A1 (de) * 2013-03-26 2014-10-02 Schaeffler Technologies Gmbh & Co. Kg Lagerung und axiale Abstützung einer Doppelkupplung an einer Getriebeeingangswelle
DE102014211633A1 (de) * 2013-07-03 2015-01-08 Schaeffler Technologies Gmbh & Co. Kg Lamellenträger für eine Doppelkupplung
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US9511661B2 (en) 2015-03-12 2016-12-06 Deere & Company Driven wheel unit including an axially compact two-speed planetary gear drive assembly
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JP6851384B2 (ja) 2016-01-29 2021-03-31 シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ 自動車用のクラッチアッセンブリおよびパワートレーン
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KR101909224B1 (ko) * 2016-11-24 2018-10-17 씨스톤 테크놀로지스(주) 이중 클러치
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CN112178069B (zh) * 2020-09-18 2021-10-29 安徽江淮汽车集团股份有限公司 静液离合器换挡执行结构、变速箱及汽车

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US20090194383A1 (en) 2009-08-06
CN101498343A (zh) 2009-08-05
CN101498343B (zh) 2013-12-18
DE102008008062B4 (de) 2014-05-22
DE102008008062A1 (de) 2009-08-06
EP2085632A1 (fr) 2009-08-05
US8413779B2 (en) 2013-04-09
EP2085632B1 (fr) 2013-07-03

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